Press for web printing having intermittent paper feeding means



y F. SLAVIC ,3,204,556 PRESS FOR WEB PRINTING HAVING INTERMITTENT Sept.7, 1965 PAPER FEEDING MEANS 1O Sheets-Sheet 1 Filed May 25. 1964 tamSept. 7, 1965 F. M. SLAVIC 3,204,556

PRESS FOR WEB PRINTING HAVING INTERMITTENT PAPER FEEDING MEANS Filed May25, 1964 10 Sheets-Sheet 2 Sept. 7, 1965 F. M. SLAVIC PRESS FOR WEBPRINTING HAVING INTERMITTENT PAPER FEEDING MEANS Filed May 25, 1964 10Sheets-Sheet 3 Sept. 7, 1965 F. M. SLAVIC 3,204,5561

PRESS FOR WEB PRINTING HAVING INTERMITTENT PAPER FEEDING MEANS Filed May25 1964 10 Sheets-Sheet 4 Sept. 7, 1965 F. M. SLAVIC 3,204,556i

PRESS FOR WEB FRI T NG HAVING INTERMITTENT PAPER EANS EDING M Filed May25, 1964 10 Sheets-Sheet 5 Sept. 7, 1965 F. M. SLAVIC PRESS FOR WEBPRINTING HAVING INTERMITTENT PAPER FEEDING MEANS Filed May 25, 1964 l0Sheets-Sheet 6 Sept. 7, 1965 F. M. SLAVIC 3,204,555

PRESS FOR WEB PRINTING HAVING INTERMITTENT PAPER FEEDING MEANS Filed May25, 1964 10 Sheets-Sheet 7 Sept. 7, 1965 F. M. SLAVIC 3,204,555

PRESS FOR WEB PRINTING HAVING INTERMITTENT PAPER FEEDING MEANS Filed May25, 1964 10 Sheets-Sheet 8 Sept. 7, 1965 F. M. SLAVIC PRESS FOR WEBPRINTING HAVING INTERMITTENT PAPER FEEDING MEANS l0 Sheets-Sheet 9 FiledMay 25. 1964 Sept. 7, 1965 F. M. SLAVIC 3,204,556

PRESS FOR WEB PRINTING HAVING INTERMITTENT PAPER FEEDING MEANS Filed May25, 1964 10 Sheets-Sheet 10 United States Patent 3,264,556 PRESS FOR WEBPRINTING HAVING INTERNIIT- TEN'I PAPER FEEDING MEANS Fred M. Slavic, NewRochelle, N.Y., assignor to Flexitron Company, New York, N.Y., apartnership Filed May 25, 1964, Ser. No. 372,139 6 Claims. (Cl. 101228)This application is a continuation-impart to my copending application,Serial No. 105,329, filed April 25, 1961 under the same title, nowabandoned.

This invention relates generally to the field of printing presses of theweb type, and more particularly to improved means for conserving paperwhere images to be printed are of dimensions less than the developedlength of the printing cylinders.

In the web type of printing press, paper is continuously fed from a rollpast a number of printing stations, each of which includes one or moreprinting cylinders which print a single color of a multicolor image insuperimposed relation. In most presses, the printing cylinder is offixed diameter, and consequently its total printing area is acorrespondingly fixed area. Where the particular image to be printed isof substantially less area, if the web of paper is fed continuously, asubstantial wastage of paper will result. This is particularly seriousin web type presses, where only long runs are usually made, and wherethe printed sheets are subsequently severed from the roll and out downto the desired size.

It is known in the art, as disclosed in my co-pending United Statespatent application Serial No. 842,806, filed September 28, 1959, to feedthe paper independently of the movement of the printing cylinders, andto accelerate mechanism moving the paper in conformance with theprinting areas of the printing cylinders to obtain a smearfreeimpression. The mechanism for accomplishing this end is relativelycomplicated and not without problems of registration, that is thealigning of subsequent impressions upon those previously printed at anearlier printing station.

It is among the principal objects of the present invention to provide animproved form of press having intermittent paper feeding means in whichthe mechanism involved may be appreciably simpler than that heretoforeknown in the art, permitting the same to be built far more compactly,and at a lower cost, together with other advantages which naturally flowfrom the employment of a simplified mechanism.

Another object of the invention lies in the provision of an improved webfeed press haying intermittent paper feeding means in which the usualloops of paper existing between stations have been eliminated, therebypermitting the press to operate at extremely high speeds withoutdifiiculty.

Still another object of the invention lies in the provision of aprinting press of the class described, and embodying the above describedadvantages, in which the paper advancement means may have relatively lowrotational inertia as contrasted with prior art devices, therebypermitting the lightening and simplification of acceleration anddeceleration mechanisms, with consequent higher speed of operation beingpossible.

Still another object of the invention lies in the provision of improvedpress construction which may be readily adjusted for the amount of feedof paper with respect to each revolution of the printing cylinders, sothat the adjustment of the press at the time of changing runs ismaterially simplified.

A feature of the invention lies in the fact that all cams comprisingparts of the embodiment are mounted upon a common hub to simplifyadjustments thereof.

3,294,556 Patented Sept. 7, 1965 These objects and features, as Well asother incidental ends and advantages, will more fully appear in theprogress of the following disclosure, and be pointed out in the appendedclaims.

In the drawing, to which reference will be made in the specification,similar reference characters have been employed to designatecorresponding parts throughout the several views.

FIGURE 1 is a side elevational view of an embodiment of the invention.

FIGURE 2 is an enlarged fragmentary side elevational view of one of theprinting stations comprising a part of the embodiment, taken at sectionr2-2 in FIGURE 3.

FIGURE 2A is a similar fragmentary side elevational view, but showingcertain of the components parts in altered relative position.

FIGURE 3 is a side elevational view as seen from the right hand portionof FIGURE 2.

FIGURE 4 is a fragmentary side elevational view as seen from the righthand portion of FIGURE 3.

FIGURES 5, 6, 7, and 8 are side elevational views showing profiles ofcertain cams comprising parts of the embodiment.

FIGURE 9 is a fragmentary sectional view as seen from the plane 99 inFIGURE 3, with certain of the component parts removed for the purpose ofclarity.

FIGURE 10 is a fragmentary view in elevation showing an alternate formof the embodiment.

FIGURE 11 is a fragmentary sectional View as seen from the plane I l-11in FIGURE 10.

FIGURE 12 is a fragmentary view in elevation showing a second alternateform of the embodiment.

FIGURE 13 is a sectional view as seen from the plane r13-13 in FIGURE12.

FIGURE 14 is a sectional view as seen from the plane 14 14in FIGURE 10.

FIGURE 15 is a fragmentary sectional view of a cam comprising a part ofeither alternate form.

FIGURE 16 is a fragmentary view in elevation showing an alternate formof meshing construction which may be used with either the alternate formof FIGURE 10 or FIGURE 12.

In accordance with the invention, the device, generally indicated byreference character 10, comprises: a frame element 11, paper Web supplymeans 12, paper Web takeup means 13, a first printing unit 14, a secondprinting unit 15, paper advancement means 16, and paper accelerating anddecelerating means 17.

With reference to FIGURE 1, the frame element 11 may be of generallyconventional construction, including a pair of parallel lower horizontalframe members 19, vertical parallel frame members 20, 21, 22 and 23,upper frame members 24, and a plurality of transverse members, one ofwhich is indicated by reference character 25.

The paper web supply means 12 includes a feeding spindie 27 supporting aconventional roll of paper 28 from which depends a Web of paper,generally indicated by reference character 29. Disposed leftwardly ofthe spindle 27, as seen in FIGURE 1, are first and second horizontallydisposed rollers 31 and 31 which are supported for rotation between theupper frame members 24 directly above a pivotally mounted bar 32. Thebar 32 describes orbital motion about an axis of rotation 33, andsupports a roller 35 for rotation about an axis 34-. Mounted between thevertical frame members 21 are first and second vertically disposedrollers 36 and 37, respectively, the periphery 38 of the roller 37 lyingin the plane of the web 29 in which the printing operation is performed.

The paper web take-up means 13 is seen in FIGURE 1, and is generallysymmetrically arranged with respect to the supply means 12. It includesfirst and second vertically disposed rollers 40 and 41, respectively,supported between the vertical frame members 22. First and secondhorizontally disposed rollers 42 and 43, respectively, are supportedbetween the upper frame members 24, and a pivotally mounted bar 44corresponds to the bar 32. The take-up spindle 45 supports a take-uproll 46 which is preferably driven at substantially uniform speed bymeans (not shown) of conventional type. As is well known in the art, thetake-up spindle 45 may also be intermittently driven by electric meanscontrolled by the location of the bar 44 through a switch (not shown).The bar 44 serves as a dancer roller for the purpose of taking up slackin the web of paper which will occur at each revolution of the printingcylinders.

The first printing unit 14 includes first and second side wall members,one of which is indicated by reference character 48, the same beinginterconnected by transverse members one of which is indicated byreference character 50. As is conventional where the web 29 is printedon both surfaces simultaneously, the side wall members 48 include anupper plate cylinder 51, an upper blanket cylinder 52, a lower blanketcylindem53, and a lower plate cylinder 54. Where means of printing otherthan conventional offset is performed, other suitable impression meansmay be provided, as the present invention contemplates application torotogravure, direct rotary printing, and the like. Gear means (notshown) interconnects the cylinders 51-54 for rotation, also as is wellknown in the art. To provide for proper registry with respect to thesecond printing unit 15, an adjusting means 56 is provided, the sameincluding a hand wheel 57 driving a threaded member 58 engaged in acorrespondingly threaded member 59, to move the entire printing unit 14longitudinally with respect to the second printing unit 15.

The second printing unit is generally similar to the first printing unit14, and includes first and second side wall members 61 and 62, toptransverse members, one of which is indicated by reference character 63,a similar upper plate cylinder 64, upper blanket cylinder 65, lowerblanket cylinder 66 and lower plate cylinder 67.

The paper advancement means 16 is incorporated into the second printingunit 15 and includes first, second and third band actuating rollers 69,70 and 71, respectively.

vTo insure synchronism of the various above described rollers, atensioned steel band 72 extends around drums on the feed rollers 36, 37,40, 41. Tension is maintained by a tensioning roller 73. As will morefully appear, the paper advancement means is driven by the secondprinting unit 15, in conjunction with the paper accelerating means 17.The band 72 extends over rollers 69 and 71 and under roller 70 as seenin FIGURE 1.

The paper accelerating means 17 performs the function of imparting anaccelerating motion to the paper advancement means 16 to bring it up tothe speed of the printing cylinders by the time the impressioncommences, and subsequently to disconnect the paper advancement meansand bring it to a rapid stop when the impression imparted by a singlerevolution of the printing cylinders has been completed.

Referring to FIGURES 2 and 3, the lower plate cylinder 67 is supportedupon a transversely disposed shaft 77, which may be driven by a primemover (not shown). The right hand end of the shaft 77 (see FIGURE 4) isprovided with a rotating cam member 7 9 having a generally planar camface 80 on the free end thereof. The second hand actuating roller 70 issimilarly mounted upon a shaft 81 disposed in paralleled relation withrespect to the shaft 77, the right-hand end being provided with apintle-like cam follower 83 on an overrunning clutch member 83'. Toposition the follower 83 within the path of the cam face 80, stop means84 cooperates with a spring 85 connected to the clutch member 83' whichnormally returns the axial position of the shaft 81 to that seen inFIGURE 4 for the commencement of a single printing cycle.

As best seen in FIGURES 3 and 9, the shaft 77 mounts a pair of radiusarms 87 and 88 which are interconnected at the free ends thereof by ashaft 89. A spring 87' urges the arm 87 in a counter-clockwise directionas seen in FIGURE 9. A gear 90 is supported upon the shaft 77. As seenin FIGURES 2 and 9, immediately leftward of the gear 90 is a rocker armshaft 92 which mounts a rocker arm 93 for pivotal movement about abearing 94. The rocker arm 93 includes a cam follower portion 95 and anactuating portion 96. An actuating cam 98 turns with the shaft 77 toimpart clockwise motion to the rocker arm 93.

At this point in the disclosure, the acceleration of the paperadvancement means 16 will be described. At the commencement of eachrotation of the printing cylinders, the cam member 79 strikes the camfollower 83 to impart a rapid accelerating movement in acounterclockwise direction as seen in FIGURE 4. By the time the cam face80 has passed the follower 83, the shaft 81 will be rotating at a speedsomewhat greater than the angular velocity of the shaft 77, but at anidentical angular velocity with the shaft 89 permitting smoothengagement of gear 99 with the gear 90. At this point the cam 98 (seeFIGURE 5), which includes an adjustable member 98' for varying itseffective length, contacts the cam follower portion 95 causing rotationof the rocker arm 93 and actuating portion 96 which act upon the radiusarm 87 to move the gear 90 on the shaft 89 into meshing relation withgear 99. At this point, the commencement of printing takes place, andcontinues for so long a time as the above-mentioned gears remain inengagement. Once the cam member 79 has passed the cam follower 83, thecontraction of the spring 85 causes rotation of the outer housing of theoverrunning clutch 83' in a counterclockwise direction, as seen inFIGURE 4, until the stop means 84 is engaged, the overrunning clutch 83'transmitting motion to the shaft 81 only in a counter-clockwisedirection, as seen in FIGURE 4.

Referring to FIGURE 2, the shaft 81 also supports a pair of radius arms100 and 101, including a connecting pintle 102 which supports apivotally mounted pawl member 103. The pawl member includes anengagement portion 104, and an oppositely disposed portion 105 having aspring 106 normally urging the same in a clockwise direction as seen inFIGURE 2. Connected to the pintle 102 is a link member 107 having apintle 108 at the lower end thereof by means of which it isinterconnected with a second link member 109 which is pivotally mountedat its lower end on a pintle 110. A cam follower 111 is mounted fororbital movement between the ends of the link member 109, and is movedby a cam 114. The link 109 is connected to a spring 113, the purpose ofwhich is to maintain follower 111 at all times in contact with cam 114.The follower 111 is periodically engaged by the cam 114 so that throughlinks 109 and 107, the link 103 is accelerated in a clockwise directionaround the gear 99, until it has obtained the same angular velocity asthe gear.

Referring again to the shaft 92, a second rocker arm 115 is provided,including a cam follower portion 116 and an actuating portion 117 havinga pintle 118 thereon. The rocker arm 115 is operated by a cam 115a (seeFIG- URE 8) which contacts a roller 124 on the cam follower portion 116to provide a clockwise motion as seen in FIG. 2. The leftward portion117 of the arm 115 imparts upward motion as seen in FIGURE 2 to anelongated link 119, and through a pintle 120, to a generallyhorizontally arranged rocker arm 121 pivoting about an axis 122. Theactuating portion 123 of the rocker arm 121 is provided with a roller124' bearing upon the upper surface of the pawl member 103.

Referring now to FIGURE 2A, at the moment when the pawl member 103 hasattained the angular velocity of gear 99, the low portion on the cam115a permits the rocker arm 116 to move in a clockwise direction underthe action of spring 126, which in turn moves link 123,

in a clockwise direction and forces engaging member 124 into mesh withgear 99'. At' the same time adjustable cam 98', acting through links 93,95, and 87, permits the gear 90' to swing in a counter-clockwisedirection out of mesh with gear 99. Control of shaft 81 is now held bymember 104 meshed in gear 99', and continued rotation of cam 114 acts todecelerate the clockwise motion of link 103 to a stop, thereby stoppinggear 99' and shaft 81. When shaft has stopped, cam 115a acts to withdrawmember 104 from gear 99'. At this point, the stop means 84 and springs85 have returned the means 16 to position for the commencement for thenext cycle.

It will be noted that cams 98', 115a, and 114 are mounted on a commonhub. Thus one angular adjustment of all three cams regulates the pointat which de celeration takes place. This in turn determines the lengthof the printed image.

From a consideration of FIGURE 1 it will be readily understood by thoseskilled in the art that as many additional printing units (not shown)may be employed as desired. Upper blanket cylinders 52 and 65 haveremovable segments on the non-printing portion of their periphery so asto release the pressure on the paper during the time that the web isstopped.

Referring now to the first alternate form of the embodiment illustratedin FIGURES and 11, parts corresponding to those of the principle formhave been designated by similar reference characters with the additionalsuflix a.

In accordance with the first alternate form, the shaft 771: rotates inbearings mounted on plates 128 and 129. Mounted on the shaft 77a areaccelerating cams 130 and 131, carrying cam blocks 132 and 141 to impartsidewise motion to a follower 142, and through links 143 and 145 to band146 and hub 147 to result in moving the serrated disc 148 axially alongthe shaft 81a. When the disc 148 is urged leftwardly, it engages teethin a serrated disc 149 which is fixed to the shaft 81a. Also mounted onshaft 77a is an adjustable cam 135 including cupped discs 136 and 137(see FIGURE and a cam section 133. The cam 135 serves to laterally movethe gear 154 through band 153, links 152 and 151, and the follower 150.The inner ring of the cam 137 is fixed on the shaft 77a, while the outerring 136 and section 133, are angularly adjustable on said shaft so asto regulate the length of the are which urges gear 154 leftwardly. Theserrated ring 155 is mounted on gear 154, so that leftward movement ofgear 154 moves the ring 155 into mesh with the serrated disc 156 whichis fixed to the shaft 81a. Cams 136, 137, 134, 138, and gear 140 aremounted on a common hub on the shaft 77a, so that one angular adjustmentwith respect to the shaft positions all of the same. Decelerating cams134 and 138 act in cooperation upon followers 159 and 160 toperiodically impart clockwise motion (see FIGURE 11) to the follower 161and serrated disc 157, as well as a return motion. The cam blocks 139and 158 which are mounted on cam 134 impart lateral motion to theserrated disc 157 through band 162, links 163 and 164, and follower 165.

At the beginning of a given cycle, shaft 81a is stationary. Referring toFIGURES 10 and 14, the cam block 132 acting through links 143, 145, and146, moves the disc 148 leftward into mesh with disc 149. Immediatelythe lobe on cam 130 moves the follower 149' mounted on the disc 148counterclockwise, as seen from the right hand portion of FIGURE 10,thereby accelerating the shaft 81:: up to the angular velocity of shaft77a, since the disc 149 is fixed to the shaft 81a. At this point, camblock 141 acts to disengage discs 148 and 149, and the follower 149returns the disc 148 to its former position through a spring 148. At themoment that disc 149 has been brought to the proper velocity, anddisconnected from disc 148, the cam 135 acts to force gear 154, and withit serrated ring 155, into mesh with serrated disc 156 which is fixed onthe shaft 81a. Since the gear 154 6 meshes with the gear 140, bothshafts are now meshed into geared relation with each other. It will benoted that gear is fixed to shaft 77a and is always meshed with gear154, so that both turn continuously.

Referring now to FIGURES 10 and 11, at the designated point in thecycle, cams 134 and 138 cooperate to accelerate in said clockwisedirection link 161 and serrated disc 157. At the moment when thevelocities of disc 157 and disc 156 are equal, cam blocks 139 and 158act to force disc 157 rightward into mesh with disc 156, while at thesame time cam 133 urges gear 154 and ring rightward out of mesh withdisc 156. Angular motion of disc 156 and with it shaft 81a is nowcontrolled by cams 134 and 138, which now act to decelerate link 161 toa stop, at which instant cam blocks 139 and 158 act to retract disc 157from disc 158. i

A useful variation to this motion can be achieved b timing cam blocks139 and 158 so as not to release disc 157 from disc 156 until the camfollower link 161 returns to its original counter-clockwise position.This has the effect not only of stopping the shaft 81, but of reversingit for a short distance after each printing cycle, enabling successiveprinted images to butt up against each other with no wasted paper inbetween.

Image size is accomplished by varying the point at which decelerationtakes place. As mentioned hereinabove, all of the pertinent cams aremounted upon a common hub, so that only one angular adjustment isnecessary.

Referring to FIGURE 12, an alternate method of meshing the main gears isdisclosed, in which the driven gear 154' is fixed to shaft 81b, andcarries serrated rings 155' and 155" fixed on either side thereof. Shafe771) carries two half gears 140 and 140", the half gear 1419" beingfixed directly to the shaft 77b, and the half gear 140 being fixed to acommon hub with decelerating cams 1341) and 1138b. Angular adjustment ofgear segment 140" with relation to segment 140 therefore changes theeffective length of gear segment which meshes with gear 154'. The effectof meshing and unmeshing shafts 77b and 81b is therefore accomplished inthe same way as previously described by means of cam 35, links 151, 152,153, etc., or by disengaging gears 90 and 99 as shown in FIGURE 9 in theprincipal embodiment.

Referring to FIGURE 16, there is shown an alternate method of shiftingthe serrated ring 155s and 1550' by means of a solenoid 166, a systemwhich is suitable where the device is operated at relatively low speeds.Electrical switches (not shown) are operated by cams.

I wish it to be understood that I do not consider the invention limitedto the precise details of structure shown and set forth in thisspecification, for obvious modifications will occur to those skilled inthe art to which the invention pertains.

I claim:

1. In a printing press unit having a printing cylinder and a feed rollerfor advancing a web of paper for an adjustable distance to said printingcylinder, the improvement comprising: first means for imparting positiveangular acceleration to said feed roller up to the surface speed of saidprinting cylinder, second means for positively maintaining said surfacespeed of said feed .roller for an adjustable period of angulardisplacement, and third means for positively decelerating said feedroller to a stop; said first means including a first shaft continuouslyrotating at the same speed as said printing cylinder, a second shaftadjacent said first shaft and connected to said feed roller, a first camon said first shaft, cam follower means, and clutch meansinterconnecting said cam follower means and said second shaft; saidsecond means including means for interconnecting and disconnecting saidfirst and second shafts in geared relationship; said third meansincluding an engaging member, a second cam for accelerating saidengaging member up to the speed of said first shaft, and a third cam forengaging said engaging member with said feed roller; continued rotationof said second cam serving to decelerate said feed roller, during whichsaid second means disconnects said geared relationship.

2. In a printing press unit having a printing cylinder and a feed rollerfor advancing a web of paper for an adjustable distance to said printingcylinder, the improvement comprising; first means for imparting positiveangular acceleration to said feed roller up to the surface speed of saidprinting cylinder, second means for positively maintaining said surfacespeed of said feed roller for an adjustable period of angulardisplacement, and third means for positively decelerating said feedroller to a stop; said first means including a first shaft continuouslyrotating at the same speed as said printing cylinder, a second shaftadjacent said first shaft and connected to said feed roller, a first camon said first shaft, cam follower means, and clutch meansinterconnecting said cam follower means and said second shaft; saidsecond means including a second cam for interconnecting anddisconnecting said first and second shafts in geared relationship; saidthird means including an engaging member, a third cam for acceleratingsaid engaging member up to the speed of said first shaft, and a fourthcam for engaging said engaging member with said feed roller; continuedrotation of said third cam serving to decelerate said feed roller,during which said second means disconnects said geared relationship.

3. In a printing press unit having a printing cylinder and a feed rollerfor advancing a web of paper for an adjustable distance to said printingcylinder, the improvement comprising: first means for imparting positiveangular acceleration to-said feed roller up to the surface speed of saidprinting cylinder, second means for positively maintaining said surfacespeed of said feed roller for an adjustable period of angulardisplacement, and third means for positively decelerating said feedroller to a stop; said first means including a first shaft continuouslyrotating at the same speed as said printing cylinder, a second shaftadjacent said first shaft and connected to said feed roller, a first camon said first shaft, cam follower means, and clutch meansinterconnecting said cam follower means and said second shaft; saidsecond means including a second cam for interconnecting anddisconnecting said first and second shafts in geared relationship; saidthird means including an engaging member, and a third cam foraccelerating said engaging member up to the speed of said first shaft,and a fourth cam for engaging said engaging member with said feedroller, continued rotation of said second cam serving to decelerate saidfeed roller, during which said second means disconnects said gearedrelationship; said second, third and fourth cams being disposed on saidfirst shaft, in mutually angularly adjustable relationship.

4. In a printing press unit having a printing cylinder and a feed rollerfor advancing a web of paper for an adjustable distance to said printingcylinder, the improvement comprising: first means for imparting positiveangular acceleration to said feed roller up to the surface speed of saidprinting cylinder, second means for positively maintaining said surfacespeed of said feed roller for an adjustable period of angulardisplacement, and third means for positively decelerating said feedroller to a stop; said first means including a first shaft continuouslyrotating at the same speed as said printing cylinder, a second shaftadjacent said first shaft and connected to said feed roller, a first camon said first shaft, cam follower means, and clutch meansinterconnecting said cam follower means and said second shaft, saidsecond means including means for interconnecting and disconnecting saidfirst and second shafts in geared relationship; said third meansincluding an engaging member, a second cam for accelerating saidengaging member up to the speed of said first shaft, and a third cam forengaging said engaging member with said feed roller; continued rotationof said second cam serving to decelerate said feed roller, during whichsaid second means disconnects said geared relationship; said second, andthird cams being disposed on said first shaft, in mutually angularlyadjustable relationship.

5. In a printing press unit having a printing cylinder and a feed rollerfor advancing a web of paper for an adjustable distance to said printingcylinder, the improvement comprising: first means for imparting positiveangular acceleration of said feed roller up to the surface speed of saidprinting cylinder, second means for positively maintaining said surfacespeed of said feed roller for an adjustable period of angulardisplacement, and third means for positively decelerating said feedroller to a stop; said first means including a first shaft continuouslyrotating at the same speed as said printing cylinder, at second shaftadjacent said first shaft and connected to said feed roller, a first camon said first shaft, cam follower means, and clutch meansinterconnecting said cam follower means and said second shaft; saidsecond means including means for interconnecting and disconnecting saidfirst and second shafts in geared relationship; said third meansincluding an engaging member, a second cam for accelerating saidengaging member up to the speed of said second shaft, and fourth meansfor engaging said engaging member with said feed roller; continuedrotation of said second cam serving to decelerate said feed roller,during which said second means disconnects said geared relationship.

6. In a printing press unit having a printing cylinder and a feed rollerfor advancing a web of paper for an adjustable distance to said printingcylinder, the improvement comprising: first means for imparting positiveangular acceleration of said feed roller up to surface speed of saidprinting cylinder, second means for positively maintaining said surfacespeed of said feed roller for an adjustable period of angulardisplacement, and third means for positively decelerating said feedroller to a stop, and reversing it for a portion of its forward motion;said first means including a first shaft continuously rotating at thesame speed as said printing cylinder, a second shaft adjacent said firstshaft and connected to said feed roller, a first cam on said firstshaft, cam follower means, and clutch means interconnecting said camfollower means and said second shaft; said second means including meansfor interconnecting and disconnecting said first and second shafts ingeared relationship; said third means including an engaging member, anda second cam for accelerating said engaging member up to the speed ofsaid second shaft, and fourth means for engaging said engaging memberwith said feed roller; continued rotation of said second cam serving todecelerate, stop, and partially return said feed roller, during whichsaid second means disconnects said geared relationship.

References Cited by the Examiner UNITED STATES PATENTS 1,978,715 10/34Meisel l0l228 2,546,372 3/51 Pinckert 101-228 2,714,268 8/55 Batteyl01228 EUGENE R. CAPOZIO, Primary Examiner.

1. IN A PRINTING PRESS UNIT HAVING A PRINTING CYLINDER AND A FEED ROLLERFOR ADVANCING A WEB OF PAPER FOR AN ADJUSTABLE DISTANCE TO SAID PRINTINGCYLINDER, THE IMPROVEMENT COMPRISING: FIRST MEANS FOR IMPARTING POSITIVEANGULAR ACCELERATION TO SAID FEED ROLLER UP TO THE SURFACE SPEED OF SAIDPRINTING CYLINDER, SECOND MEANS FOR POSITIVELY MAINTAINING SAID SURFACESPEED OF SAID FEED ROLLER FOR AN ADJUSTABLE PERIOD OF ANGULARDISPLACEMENT, AND THIRD MEANS FOR POSITIVELY DECELERATING SAID FEEDROLLER TO A STOP; SAID FIRST MEANS INCLUDING A FIRST SHAFT CONTINUOUSLYROTATING AT THE SAME SPEED AS SAID PRINTING CYLINDER, A SECOND SHAFTADJACENT SAID FIRST SHAFT AND CONNECTED TO SAID FEED ROLLER, A FIRST CAMON SAID FIRST SHAFT, CAM FOLLOWER MEANS, AND CLUTCH MEANSINTERCONNECTING SAID CAM FOLLOWER MEANS AND SAID SECOND SHAFT; SAIDSECOND MEANS INCLUDING MEANS FOR INTERCONNECTING AND DISCONNECTING SAIDFIRST AND SECOND SHAFTS IN GEARED RELATIONSHIP; SAID THIRD MEANSINCLUDING AN ENGAGING MEMBER, A SECOND CAM FOR ACCELERATING SAIDENGAGING MEMBER UP TO THE SPEED OF SAID FIRST SHAFT, AND A THIRD CAM FORENGAGING SAID ENGAGING MEMBER WITH SAID FEED ROLLER; CONTINUED ROTATIONOF SAID SECOND CAM SERVING TO DECELERATE SAID FEED ROLLER, DURING WHICHSAID SECOND MEANS DISCONNECTS SAID GEARED RELATIONSHIP.